Fluid pressure brake



Jufiy 3% 1935. v v c. c. FARMER 2,009,843

FLUID PRESSURE BRAKE Ori inal Filed Nov; 1, 1952 AUXILIARY RES.

' as? INVENTOR CLYDE QFARMER ATTORN BRAKE CYLINDER Patented July 30, 1935 UNITED STATES FLUID PRESSURE BRAKE Clyde '0. Farmer, Pittsburgh, Pa'.,assignor to The Westinghouse Air Brake Company, flilrner ding, 'Pa;, a corporation of Pennsylvania Application November 1, 1932, Serial No 6%,645 Renewed March-3, 193 i 11' Claims (o1. soa -74) This invention relates to fluid pressure brakes more particularly to the type adapted to 0perate to apply and release the brakes in'accordance with variations in brake pipe pressure.

It heretofore been proposed to provide a fluid pressure brake equipment having means controlled by the substantially constant pressure of fluid in a control reservoir, for governing the pr ssu e in the brake cylinder in efiectingan applica n a release of the brakes, so that the brake cylinder pressure will be properly proportional to the degree of reduction or increase in brake pipe pressure, regardless of leakage of fluid under pressure from the brake cylinder, Within a permissible degree, and-regardless of varia ticns in travel of the piston in the brake cylinder.

ful

[in nnent of the above character is dis closed in my pending application, Serial No. 191, filed August 31, 1932, and according to pend ng application, the control reservoir,

is charged with fluid at the pressure carried he brake pipe while the brakes are release s immediately isolated from the source of fluid pressure supply upon initiating a reduction Jake pipe pressure, so that the pressure of in reservoir will remain constant while are applied and thus govern the degree -e acting in the brake cylinder.

in. controllinga train down a long descending grade it is customary, after initially applying the brakes, to recharge the brake system in order to be able to effect another application of the brakes. Whi e the brake system is being recharged, the brake on the train are being released and in order to prevent the train from accelerating to a degree beyondcontrol during the rechargingperiod, it cJ lly necessary to eflect another application rakes before the initial application is completely released and before the brake system is recharged.

mince, in the br'akeequipment disclosed in the above mentioned pending application, 'thecontrol SN Oil. is adapted to be chargedionly'whe'n the equipment is substantially'fully charged, which i set likely to occur whendescendin'g a grade, any

leak of fluid under pressure from the'control ir during the grade descendingperiod res control reservoir pressure so that after the initial application of brakes,ithe brakecylinder prepa e obtained upon a furth'erapplication will 1 intended by a degree proportionate Lee at reduction in the control reservoir ire. In case of severe leakage of fluid under ressure from the control reservoir on some cars in a train,the brake cylinder pressure obtained on those cars upon a reapplication of the brakes mightbe so-low as to be of little or novalue, other cars where there was no leakage of Ed under pressure from the control reservoir the intended brake cylinder pressure would be obtained, while on still other cars where intermediate degrees of leakage of fluid under pressure from the control reservoir was eflective, the brake pressure obtained would vary from the value intended to thelow or practically useless value. The result of these varying pressures in the brake-cylinders on the train might only result in excessive wear of the wheels and brake shoes on certain cars in the train, but atsome time the loss of brake cylinder pressure might be so severe throughout the whole train as to permit the train to get out of control and possibly resul ina wreck. One object of my invention is to provide an improved fluid pressure brake equipment in which spring means are employed to control the brake cylinder pressureobtained upon effecting an application of the brakes, in order to obviate the above undesirable condition. 7 7 Another object of my invention is to provide an improved fluid pressure brake equipment having spring means for controlling the brake cylinder pressure obtained upon effecting an application of the brakes, means for automatically adjusting the pressure of saidspring means when the brake system is fully charged with fluid under pressure and means for automatically locking the spring means in the adjusted condition. upon initiating an application of the. brakes, so that the control pressure of said spring means will remain constant for an indefinite period, as is required in the descent of a long grade.

According to this last'object, the spring means will beadjusted according to the brake pipe pressure carried, such, for example, as seventy, ninety or one hundred ten pounds, as well as according to the brake pipe pressure existing in various parts of the train, as controlled by leakage conditions inthe train. In an equipment of this character, the brake cylinder pressurecontrol device is governed byvariations in opposing fluid pressures, and when thebrake cylinder pressure, which is generally one of the control pressures, is reduced to a low degree, such, for instance, as five pounds or less, it is diflicult at times :to obtain suflicient diirerential between the control pressures to ensure Another object of my invention is to provide improved means for obviating the last described undesirable condition.

Other objects and advantages will appear in the following more detailed description of the invention.

In the accompanying drawing; Fig. 1 is a diagrammatic view, mainly in section, of a fluid pressure brake equipment embodying the invention; Fig. 2 is a sectional view taken on the line 2-2 of Fig. 1; Fig. 3 is a sectional view taken on the line 33 of Fig. 1; Fig. 4 is a sectional view taken on the line 4-4 of Fig. l; and Fig. 5 is a diagrammatic view of a portion of the valve device shown in Fig. l and showing the empty to load changeover valve in the load position.

As shown in the drawing, the invention is pref erably associated with an empty and load fluid pressure brake equipment which is quite similar in many respects to the fluid pressure brake equipment disclosed in my pending application hereinbefore referred to and comprises a pipe bracket 1, an application valve mechanism 2 mounted on one face of pipe bracket l against a gasket 4, a brake cylinder pressure control valve mechanism 3 mounted on another face of said pipe bracket against a gasket 5, an auxiliary reservoir 6, an empty brake cylinder I, a load reservoir 8, and a load brake cylinder 9.

The application valve mechanism 2 comprises a triple valve device I9, an inshot valve device H and associated therewith is an empty and load change-over valve device l2.

The triple valve device l9 comprises a casing containing a piston I3 forming at one side, in conjunction with a face of the pipe bracket l, a chamber 54 connected through a passage [5 to a brake pipe l6 and forming at the opposite side a valve chamber l1 communicating with the auxiliary reservoir 6 through passage and pipe l8 and containing a slide valve 29 and a pin type graduating valve 23 slidably mounted in a suitable bore in one end of the slide valve and adapted to control communication from valve chamber H to a passage 24 in slide valve 29. The piston I3 is provided with a stem [9 extending into chamber I! for operating the slide valve 29 and a pin 25 carried by said stem operatively connects the graduating valve 23 to said stem.

The inshot valve device Ii comprises a. check valve 26 contained in a chamber 21, a spring 28 contained in said chamber and engaging check valve 26 for urging said check valve into sealing engagement with a seat rib 29, a piston 30, and

a stem 3i projecting from said piston and adapted to be operated thereby to move the check valve 26 away from seat rib 29.

A sealing gasket 32 is secured to one face of the inshot valve piston by means of a clamping nut 33 having screw-threaded engagement on the stem 3| at the base thereof. The other face of the inshot valve piston 39 is open to a chamber 34 which is at all times vented to the atmosphere through a passage 35 and which contains a spring 36 acting on said piston for urging said piston to its normal position in which gasket 32 effects a seal against the casing and the check valve 26 is unseated by stem 3|. The stem 3| slidably operates through a suitable bore in a partition wall 31 forming at one side a chamber 38 and at the opposite side a chamber 39. Chambers 38 and 39 are in constant communication through passages 40 and 4|.

The empty to load change-over valve l2 comprises a casing, a plug valve 42 rotatably mounted in said casing, and a manually operated handle 43 for turning said plug valve from empty position, as shown in Fig. 1, to load position, as shown in Fig. 5, and reverse. The plug valve 42 is subject over its larger end to the pressure of fluid in a chamber 44 which is adapted to be supplied with fluid under pressure from the triple valve chamber l'l through passages 45 and 46. A spring 41 in chamber 44 acts on the plug valve 42 to hold said plug valve seated when the brake sys- 'tem is not charged with fluid under pressure.

The brake cylinder pressure control mechanism 3 comprises a casing made up of five sections 48, 49, 56, 5|, and 52, these casing sections being all secured together in the order listed and then, as a unit, secured to the pipe bracket l against the gasket 5.

A flexible diaphragm 53 is clamped between the casing'sections 38 and 49 and has at one side a chamber 54 which is open at all times to the auxiliary reservoir 6 through passage 55 and passage and pipe 18. and has at the opposite side a chamber 56 which is at all times open to the empty brake cylinder 1 through passages 51 and 58. The opposite side of the brake cylinder chamber 56 is formed by a flexible diaphragm 59 clamped between the casing sections 49 and 50, the opposite side of the flexible diaphragm 59 being exposed to atmospheric pressure in a chamber 69 formed in the casing section 50 and vented to the atmosphere through an opening 6|.

Disposed in the atmosphere chamber 60 and engaging one side of diaphragm 59 is a follower member 62 having a stud portion 63 extending through said diaphragm into chamber 56. follower plate 64 is applied over the stud 63 to the opposite side of diaphragm 59 and-is secured in position by means of a nut 65 having screwthreaded engagement with said stud.

The follower member 62 is adapted to engage a stop 66 in the casing section 50 for limiting the deflection of diaphragm 59 in an upwardly direction, while the follower plate 64 is provided with an annular rib 61 adapted to engage an annular rib 68 formed in the casing section 49 for limiting the deflection of diaphragm 59 in the opposite direction. In order that the follower member 62 and follower plate 64 be properly spaced so as to govern the diaphragm deflection, just described, the follower plate 64 is provided around the aperture containing stud 63 with an annular rib 69 adapted to engage the follower member 52 and thus properly position the follower member 62 and follower plate 54 with respect to each other. The thickness of the diaphragm 59 is sufficiently greater than the depth of rib 69, however, to ensure leak-proof compression of said diaphragm.

A follower plate 10 is disposed in chamber 56 on one side of diaphragm 63 and is provided with a stud H extending through said diaphragm into chamber 54. A follower plate '72 contained in chamber 54 is applied over the stud i I, and a nut 13 having screw-threaded engagement with said stud is provided to securely clamp the follower plates 10 and 12 to said diaphragm. The follower plate 10 is provided with a plurality of upwardly extending struts 14 normally engaging the follower plate 64 for transmitting pressure from diaphragm 53 to diaphragm 59.

The casing section 49 is provided with a lug '15 extending into the chamber 56, said lug being provided with a passage 76 terminating at one end in a chamber 11 and at the opposite end in a chamber 18, the open end of chamber 18 being positioned substantially centrally below the stud portion 63 of the follower member 62.

Screwed into the open end of chamber I8 is a valve seat plug I9 having a chamber containing a ball valve adapted to seat on a taperedseat formed in said plug. A spring 8! is provided in chamber '18 for urging the ball valve 89 into engagement with its seat. Secured in the ball valve 80 is a pin valve 82 which extends through a relatively large passage in the valve seat plug 19 and into a passage 89 formed in the stud 63, the passage 83 being also relatively large in diameter as compared to the diameter of the pin valve so as to permit flow of fluid under pressure through said passages. In the passage 83 a valve seat 84 is provided and is adapted, under certain conditions, to be moved into engagement with the pin valve 82, the area of the opening through said Valve seat being reduced to a predetermined size by means of a choked passage 85.

In Fig. 1 of the drawing, the pin valve 82 is shown unseated and the follower member 62 engaging the stop 66 in the casing section 53. The limited deflection of the diaphragm 59 from the position shown in the drawing to the position in which follower plate 54 engages the rib 68 is adapted to move the valve seat 84 into engagement with the pin valve 82 and then oper ate the pin valve 82 to unseat the ball valve 89 and it will therefore be evident that when the diaphragm 59 is deflected to an intermediate position both the pin valve 82 and ball valve 89 will be seated.

A valve seat plug 85 is screwed into the casing in the open end of chamber "I? formed in the lug 15. Said plug is provided centrally with I an opening 81 leading to a tapered valve seat and a ball valve 88 contained in chamber I1 is pressed into engagement with said seat by means of a spring 89.

According to the invention, a sleeve 99 is mounted on the follower member 62 which'is secured to the upper side of the diaphragm 59. This sleeve 96 is adapted to telescope with another sleeve 9! the outer end of sleeve 9I being closed to form a follower member engaging one side of a flexible diaphragm 92- which is clamped between the casing sections 59 and SI. One or more springs 93 and 94 are contained in thea chamber formed within the sleeves 99 and 9! and engage the follower member 62 and the closed end of the sleeve 9I. These springs are preferably contained in the sleeves 90 and SI under compression and in order to prevent the sleeves from being pushed apart, particularly in assembling the apparatus, two screws 97 are provided, diametrically opposite each other in the sleeve 9!, each of said screws having an extension 98 projecting into an elongated slot 99 provided through the side wall of sleeve 99. I V

The opposite side of diaphragm 92 is open to a chamber communicating through passages 95 and I8 with the auxiliary reservoir 6. The movemerit of the diaphragm 92 into chamber 95 is limited by the screws 91 in the sleeve 9| so that auxiliary reservoir pressure will act over the full area. of said diaphragm. In case the diaphragm should swell or thicken due to contact with oil, its deflection into chamber 95 is adapted to be limited by engagement with a, plurality of ribs I 59 formed in the casing section 5| so as to positively ensure that fluid from the auxiliary reservoir may act on the full area of said diaphragm. When the brake system is fully charged, the

- pressure of fluid in the auxiliary reservoir, acting in chamber 95 on'thediap'hragm 92' compresses the springs 93 and 94 unti1, their pressure is equivalent to the auxiliary reservoir pressure; The

pressure exerted byflthese springs on the follower member 62' correspond-s to the pressure exerted on a corresponding member by the constant pressure of the fluid in the control reservoir in the pending application hereinbefore mentioned. In order that the pressure of the springs 93 and 94 will not be reducedwhen the auxiliary reservoir pressure is reduced on diaphragm 12 in effecting an application of the brakes, means are provided for locking said springs in their adjusted position immediately upon initiating an application ofthe brakes and then maintaining them locked in their adjusted position until the brakes are substantially fully released, as will now be described;

The sleeve Si is provided withtwo lugs or fulcrum pins Iiil arranged diametrically opposite each other and pivotally mounted on the pins II are the arms I92 of a lever member 483. The outer end of each of the arms M32 is provided with a, fulcrum pin I94 pivotally extending into a suitable bore in the casing section 59. o The opposite end of the lever member. N33 is pivotally connected to one end of a rack Hi5 slidably mounted in a suitable bore in the casing section 5i and extending into a chamber Hi6 formed in the casing section 52 and slidably engaging a surface I87 in chamber I96. It will be evident that as the springs 93 and 94 are compressed to the value of the auxiliary reservoir pressure acting in chamber 95 on diaphragm 92, th rack I95 will be moved or adjusted toa corresponding position through-the movement of the sleeve 9! and the medium of the lever member I83.

In order to lock the rack 35in the adjusted position upon initiating an application 'of the brakes, a detent I 98 is slidably mounted in a suitable opening through a lug see projecting from the casing section 52, and isprovided with teeth H9 adapted to efiect locking engagement With-correspondingteeth on the rack M35. The detent is preferably square or rectangular in cross section and the opening through lug I iii in which the detent is slidably mounted is of the same shape so as to maintain the teeth onthe detent aligned with the teeth on the rack m5. The detent 98 is provided. with a rearwardly projecting extension III through the medium of which the detent is adapted to be moved into and out of locking engagement with the rack I95. For pulling the'detent 5 98' out of locking engagement with the rack 95, a spring 5! 8 is interposed between-a collar H9 mounted on the extension II I and a washer I20 which is mounted over theextension I i I and engages the lug I69.

For urging-the detent into locking engagement o with the rack I05 against the opposing pressure of spring II8, the end of the extension III is pivotally connected to one arm of a bell crank lever II2 which is'pivotally supportedon a lug II3 projecting from the casing section The other arm of the bell crank lever IIZis pivotally connected to one end of an operating bar IN. The opposite end of the'operating bar I I4 is pivotally connected to one end of a lever bar II5 which is pivotally carried by a lug I It projecting from the casing section 52.

The operating bar H4 is provided intermediate its ends with a fulcrum pin I I7 whichis carried in a slot formed in one end of ameniber I43.

The member I46 slidably extends through a' suitable bore in one wall of the casing section 52 into a chamber I2| wherein said member is associated with a, follower plate I22 carried on one side of a flexible diaphragm I23. The chamber I2I at the side of the diaphragm I23 containing the follower plate I22 is at all times open to the atmosphere through a passage I24, chamber I06, through an opening I25 provided in the casing section 5| for operation of a link I26, which will be hereinafter described, and from opening I 25 through chamber 60 and atmospheric opening 6|. The diaphragm I23 is open at the opposite side to a chamber I21 adapted to be supplied with fluid under pressure through a passage I28 leading to the seat of slide valve 20 in thetriple valve-device I0. The deflection of diaphragm I23 by fluid under pressure supplied to chamber I21 is adapted to be limited by engagement of the follower plate I22 with an annular shoulder section 52.

The end of the lever bar II5, opposite to the end connected to the operating bar H4, is pivotally connected to one end of a link I30 the opposite end of which is pivotally connected to one end of a lever I3I. The lever I3I is pivotally carried on a lug I32 depending from a cover I33 secured to the casing section 52 for closing the open end of chamber I06. One end of the link I26 is pivotally connected to the other end of lever I3I while the other end of said link is pivotally connected to one end of a lever I34 pivotally carried by a lug I35 projecting from casing section 50. The other end of the lever I34 is forked to provide two arms I36, one of said arms extending around one side of the sleeve and the other of said arms extending around the other side of sleeve 90. Each of the arms I36 is provided adjacent its end with a hook-like portion I31 adapted normally to engage with a pin' or lug I38 projecting from the sleeve 90, the two pins I38 being arranged on the sleeve 90 diametrically opposite each other.

The casing section 52 is provided with a lug I39 having a cavity I40 for holding one end of a release bias spring I4l, while the other end of said spring engages the lever I3I in a cavity I42 formed in said lever and at all times exerts a pressure on the lever I3I tending to rotate said lever in a counterclockwise direction, and the pressure of said spring acting through the lever I3I, link I30 and lever bar |I5 on the operating bar 4 exceeds the opposing pressure of spring I I8 acting through the bell crank lever M2 on the operating bar M4 for reasons which will be hereinafter described.

In order to maintain looseness in the pivot connection of the lever member I03 to the casing section 50, the sleeve 9! and rack bar I95, taken up in the direction of compressing the springs 93 and 94, a light tension spring I43 is connected between one end of the rack I05 and a finger I44 projecting from the side wall of the casing section 59.

The empty brake cylinder 1 and the load brake cylinder 9 may be of the usual well known type, such as fully described in the pending application hereinbefore mentioned, and since the operation of these brake cylinders does not enter into the invention it is deemed unnecessary to provide a more detailed description.

In operation, in initially charging the fluid pressure brake equipment, fluid under pressure supplied to the brake pipe IS in the usual well known manner, flows from said brake pipe through passage I5 to the triple valve piston I29 provided in the casing chamber |4. -With the triple valve parts in the release position, as shown in the drawing, fluid under pressure supplied to piston chamber I4 flows through a feed groove I45 to the slide valve chamber I1 and from thence through passage I8 to the auxiliary reservoir 5 thus charging the auxiliary reservoir with fluid at the pressure carried in the brake pipe.

Fluid at the pressure in the auxiliary reservoir 6 flows from the auxiliary reservoir passage I8 through passage 55 to diaphragm chamber 54 and through passage 96 to diaphragm chamber in the brake cylinder control mechanism 3. The pressure of fluid in diaphragm chamber 54 deflects the diaphragm 53 upwardly moving the struts 14 into engagement with the follower plate 64. The pressure of fluid in diaphragm chamber 95 deflects the diaphragm 92 downwardly until the springs 93'and 94 are compressed to a degree Where their reaction is equivalent to the pressure applied by the diaphragm 92, hence the pressure exerted by said springs upon the follower member 62 is equivalent to auxiliary reservoir pressure acting upon the diaphragm 92.

The diaphragms 53 and 92 are of the same area, likewise the area of the follower plate 10 and the closed end of the sleeve 9| engaging diaphragm 92 are of the same area, so that the pressure exerted on the springs 93 and 94 and hence on the follower member 52 equals the opposing pressure applied through the medium of the diaphragm 5 3.

The diaphragm chamber I21 being initially vented, as will be hereinafter described, the diaphragm follower I23 and stem I46 are in their lower position which permits spring H8 to hold the teeth I I0 of the detent I08 out of engagement with the rack I95 so that said rack may move as the sleeve 9| is moved in compressing the springs 93 and 94. Also the pressure of spring |4| acting on the lever I3! is adapted to apply pressure through said lever, link I26, and lever member I34 upon the pins I38 in the sleeve 90. Since the pressure of springs 93 and 94 just equals the opposing pressure of fluid in chamber 54 acting on diaphragm 53, the pressure of spring I4I applied to the sleeve 99 provides a bias which holds the sleeves 99 and 9| in the release position in which the follower member 62 engages the stop 66.

In the release position of the sleeves 90 and 9| and follower member 92, the seat 84 is moved away from the pin or release valve 82 so that the brake cylinder chamber 56 is vented to the atmosphere through passage 83, the choked passage 85, chamber I41 within the sleeves 90 and 9!, opening I48 through the sleeve 90, chamber 60 and opening 6|. The empty brake cylinder 1 being connected through pipe and passage 58 and passage 51 to the brake cylinder chamber 56 is also vented with said chamber. 7

The brake cylinder passage 51 is connected by passage 40 to chamber 38 in the inshot valve device II and by passage 4| to chamber 39 at one side of the inshot valve piston 30, so that both chambers 38 and 39 are vented, and due to chamber 39 being vented, spring 36 is permitted to hold the piston 30 in the position shown in the drawing in which the gasket 32 seals on the casing and the check valve 26 is unseated so that chamber 21 is opened to chamber 38 and thus also vented.

A passage I49 is connected to the vented chamber 21 and leads to the seat of the triple valve slide Valve 20. With the slide valve 20 in release position, the diaphragm chamber I 21 is vented through passage I28, and a cavity lill-insaid slide valve, which cavity connects passage I28 to the vented passage 9, also a quick service reservoir I5I is vented through passage 9 by way of passage I52 which is connected to passage I49 through a cavity I53 in slide valve 20.

With the empty to load change over valve device sI2 in the empty position, as shown in the drawing, the load reservoir 8 is vented to the atmosphere through pipe and passage I 54, a cavity I'55' in the plug valve 42 and an atmospheric passage 1'56, whilethe load brake cylinder 9 is also vented to the atmosphere through pipe and passage I51, cavity I55 in the plug valve 42 and atmospheric passage I56. With the empty to load change over valve device I2 in this empty position only the auxiliary reservoir 5 and empty brake cylinder I are effective, while if the empty to load change over valve device it is in 'the load position, as shown in Fig. 5,...the load reservoir 8 and load brake cylinder 9 are also effective. 'This operation is fully described in the pending application hereinbefore mentioned and since,

- insofar as the invention is concerned, the operation of the brake equipment is the same in both positions of the empty to load change over valve, it is deemed unnecessary to hereinafter describe the operation of the equipment when the empty to load change over valve device I2 is in the load position.

If it is desired to effect an application of the brakes, the pressure of fluid in brake, pipe I6 and triple valve piston chamber I4 is reduced in the usual. manner and upon obtaining a sufficient diiferential between the pressure inpiston chamber 14 and valve chamber H, the piston I3 is moved outwardly to application position in which it engages the gasket 4. This movement of the piston i3 first pulls the graduating'valve 23 away from its seat in slide valve 20, then shoulder 2| on the piston stem I9 engages the end of and moves the slide valve .to application position.

In application position of the slide valve 20, cavity I53 connects the brake pipe passage I5 to passage I52 leading to the quick service reservoir 15.! so. that fluid under pressure is permitted to flow from the brake pipe I6 to said reservoir and effect alocal quick service reduction in brake pipe pressure for accelerating serially the operation of the triple valves throughout the train, in the usual well known manner.

With the slide valve 2.0 in application position fluid at auxiliary reservoir pressure flows from valve chamber H to passage I28'and from thence to diaphragm chamber I21 and acts on the. diaphragm I23 which is. quickly deflected upward- 1y to. the position defined by engagement of the follower plate I22 with shoulder I19. This deflection of diaphragm I 23 moves the fulcrum pin III upwardly and since spring Ill exerts a great.- er pressure on one end of the operating bar 116 than spring I I8 exerts on the. other end, the operating bar I I4 initiallyful'crums on the pivat, pin I58, connecting to lever bar H5 and opcrates the bell crank lever I I2 to move the detent. {98 against spring I I8. until the teeth I III on said detent effect locking engagement with the correspondingteeth on the rack. After the detent moved into locking engagement with rack I95, the pivot pin I59 connecting the bell cranklever M2 to the operating :bar II4 becomes a ful'crwn so that further deflection of the diaphragm I23 and .consequentmovement of the fulcrum pin II1 operates the lever bar H5, link I30, lever I3I, .link I26 and lever I34 against the pressure of spring I until, at the time the followerp'late I22 engages shoulder I29, the hooked portions I 37 of the arms I35 of lever I34 are moved out of engagement with and away from the pins I38 in the sleeve 90, thus removing from sleeve 90 the pressure of the bias spring I4I.

At the same time as fluid under pressure is supplied to diaphragm chamber IZI for operating detent I 08 to lock the rack I05 so as to maintain the control springs 93 and'Sd in their adjusted position and for removing the pressure of bias spring Hi from the sleeve 90, fluid under pressure is also supplied from the auxiliary reservoir E through the valve chamber I1, port Ed in the slide valve 20 to passage I 49 leading to chamberZI, thence past the normally unseated check valve 26 to chamber 38 and from chamber 38 through passages 49 and 51 and passage and pipe '58 to the empty brake cylinder i. As fluid under pressure flows through passage 5-1 to the empty brake cylinder I, fluid also flows from said passage to chamber 56 in the brake-cylinder pressure control valve mechanism 3 and through passage to chamber 39 at one side of the inshot valve piston 36.

When the pressure obtained in the empty brake cylinder I .and chamber 39 acting on the inshot valve piston 30 is thus built up to a predetermined degree, such as ten pounds, the pressure of spring 36 is-overcome and the inshot valve piston 30 is moved outwardly. The initial movement of the piston 39 breaks the seal between the gasket 32-and the casing thereby exposing the full area of said piston to brake cylinder pressure acting in chamber 39 which causes prompt movement of said piston into sealing engagement with a gasket IB-I, whereupon spring 28 seats the check valve so that the continued supply of fluid under pressure to the brake cylinder can only occur at a restricted rate through a choked passage I82 connecting the supply passage I49 to chamber 38.

The-initial inshot of fluid under pressure to the brake cylinder past the check valve 26' is at a rapid rate to provide for prompt operation of the brake cylinder piston I68 to move the usual brake shoes (not shown) into engagement with the car wheels (not shown), after which, the supply of fluid to the brake cylinder is restricted by the choked passage I62 to provide a gradual application of the brakes.

In effecting an application of the brakes as just described, whena slight reduction in auxiliary reservoir pressure is obtained, this reduction being effective in diaphragm chamber 54 on the diaphragm 53 reduces the pressure on said diaphragm below the opposing pressure of the control springs 93 and 94 so that said springs move the follower member $2 downwardly. This movement of the follower member 62 shifts the release valve seat 84 into engagement with the release valve 82 so as to prevent the venting of fluid under pressure from chamber 58 and the empty brake cylinder 1, which is connected to chamber 56 through passage and pipe '58 and passage 57, to the atmosphere by way of chame ber 16'! within the sleeves 90. and 9!, opening I48, chamber 60 and opening BI.

The auxiliary reservoir 6' is so proportioned to the volume created in theempty brake cylinder 1 by a predetermined or standard movement of the brake cylinder piston I60 as to provide a certain reduction in auxiliary reservoir pressure, as for instanca'each pound reduction in auxiliary reservoir pressure will provide two and one half pounds pressure in the brake cylinder which pressure is also effective, in chamber 55. If the movement of the empty brake cylinder piston is standard, then the increase in pressure in chamber 55 acting on the differential areas of diaphragms 53 and 59 compensates for the reduction in auxiliary reservoir pressure in chamber 54, so that the movement of the follower member 52 by springs 93 and 94 ceases upon seating of the release valve 82.

If, however, the movement of the empty brake cylinder piston IE is less than the standard, the brake cylinder volume is also less, and consequently the same amount of fluid under pressure from the auxiliary reservoir produces a higher brake cylinder pressure than if the brake cylinder volume were standard. Under this condition, the higher than standard brake cylinder pressure obtained in chamber 55 and acting on the differential areas of diaphragms 53 and 59 unbalances the opposing forces on said diaphragms and aided by auxiliary reservoir pressure in chamber 54 acting on diaphragm 53 deflects said diaphragm upwardly against the constant pressure of springs 93 and 94. The resultant movement of the release valve seat 85 away from the release valve 82 permits fluid under pressure to be vented from chamber 55 and theempty brake cylinder '1 to the atmosphere until the pressure in said chamber and the empty brake cylinder is reduced to the proper relation to the reduction in auxiliary reservoir pressure acting in chamber 54. When the brake cylinder pressure is thus reduced to the proper relation with respect to the reduction in auxiliary reservoir pressure, the constant pressure of control springs 93'and 94 moves the follower member 62 back to the position in which seat 84 engages the release valve 82 so as to prevent further venting of fluid under pressure from the empty brake cylinder.

If the movement of the empty brake cylinder piston I60 is greater than standard, the brake cylinder volume is also greater, so that the pressure obtained in the brake cylinder is lower than that which would be obtained if the movement of the piston were standard. Under this condition, the brake cylinder pressure acting in diaphragm chamber 56, plus the auxiliary reservoir pressure acting in diaphragm chamber 54 is inadequate to balance the opposing and constant pressure of the control springs 93 and 94, so that after seating the release valve 82, the diaphragms 59 and 53 are further deflected by said springs and operate through the release valve 52 to unseat the ball check valve 80 against the opposing pressure of the light spring 8!, w rereupon fluid under pres-.

sure, flows from the brake pipe 6 to the brake cylinder I by way of pipe and passage [5, chamber I63, opening 87, past the check valve 88, through passage 16, and chamber 18, and then past the unseated ball check valve 89 to chamber 56 and the empty brake cylinder 1. Fluid under pressure is thus supplied from the brake pipe IS to the empty brake cylinder 1 until the pressure obtained in said brake cylinder and in diaphragm chamber 55 is increased to the, proper value relative to the reduction in auxiliary reservoir pressure. When this proper relation between brake cylinder pressure and auxiliary reservoir pressure is obtained, these pressures acting on diaphragms 53 and 59 move said diaphragms against the opposing and constant pressure of the'con trol springs 93 and 94 and permit the ball check valve 89 to seat so as to prevent further flow of fluid under pressure from the brake pipe to the brake cylinder.

If the pressure in the empty brake cylinder and diaphragm' chamber 55 should reduce due to leakage, the equilibrium of pressures on the diaphragms 53 and 59 will be destroyed and permit the pressure of the control springs 93 and 94 to deflect said diaphragms and unseat the ball check valve 80 so as to permit fluid under pressure to be supplied from the brake pipe to the brake cylinder to compensate for said leakage, in the same manner that fluid under pressure is supplied from the brake pipe to the brake cylinder in case ofexcess travel of the brake cylinder piston IGI.

If the brake pipe pressure is reduced to below the-pressure at which the auxiliary reservoir equalizes into thebrake cylinder I, it will then be evident that the pressure in said brake cylinder can not be maintained from the brake pipe. Under such a condition, the ball check valve 8'! will be unseated as above described and in order to prevent the flow of fluid at the higher pressure in the empty brake cylinder and chamber 56 past the check valve 89 to the lowerpressure in the brake pipe, the ball valve'88 is pressed into engagement with its seat by means of spring 39 and brake cylinder pressure acting in chamber 11.

In order to eiTect a release of the brakes after an application, fluid under pressure is supplied to the brake pipe i6 and piston chamber M of the triple valve device Hi. When the pressure in piston chamber 14 is thus increased a predetermined degree above the auxiliary reservoir pressure in valve chamber [1, the piston i3 is operatedv and seats the graduating valve 23 and then moves the slide valve 20 to release or charging position, as shown in the drawing.

When the slide valve 29 moves to release position, the application port 24 is moved out of registry with passage 9 through which fluid under pressure was supplied to the empty brake cylinder, '1 in eifecting an application of the brakes, and diaphragm chamber IN is connected to said passage through passage I28 and cavity 255 in slide valve 29 so that brake cylinder pressure becomes effective on the diaphragm I23 to maintain the detent I58 in looking engagement with the rack 505 and also'to maintain the. bias spring I4! compressed and therefore ineffective. The quick service reservoir [5! is also placed in communication with the brake cylinder passage M9 through passage !52 and cavity I53 in slide valve 25. These communications are established so that the pressure of fluid in diaphragm chamber I21 and in the quick service reservoir l5l reduces withthe pressure in the empty brake cylinder upon releasing fluid under pressure from said brake cylinder, as will now be described.

In the release position of the triple valve de vice, fluid under pressure supplied from the brake pipe 25 to piston chamber 14 flows through feed groove I45 to valve chamber I! and from thence through passage and pipe !8 to the auxiliary reservoir 6. Fluid under pressure also flows from passage 58 through passage 96 to diaphragm chamber 95 and through passage 55 to diaphragm chamber 54.

v The increase in auxiliary reservoir pressure in chamber 55 acting on diaphragm 53, plus th brake cylinder pressure in'chamber 55 acting on the difierential areas of diaphragms 59 and 53 overcomes the opposing, constant pressure of springs 93 and 9t and deflects the diaphragms 53 and 5d upwardly, thereby moving the release valve seat 3 out of engagement with the release valve 82, which permits fluid under pressure to be released from the empty brake cylinder I through pipe and passage 58, passage 51, chamber the release valve 82 to chamber llwithin the sleeves 30 and 9|, through opening I 58, chamber 5% and opening 6| to the atmosphere. The rate at which fluid under pressure can be thus released from the empty brake cylinder is controlled by the flow area of choked passage 85, said choke-d passage being smaller than the flow area of openings M8 and Si, so iliu'd under pressure vented through chambers 54'! and 63 is not permitted tobuild up a pressure on diaphragm 59 and influence the control of said diaphragm by the constant pressure of springs 93 and 34;

In order to graduate the release of the brakes, the increase in brake pipe pressure, and con.- sequently the increase in pressure in the auxiliary reservoir 5 and diaphragm chamber 54, is limited to an amount governed by the degree of release desired. I

The brakecylinder pressure control mechanism 3 responds to the increase in auxiliary reservoir pressure to vent fluid under pressure from the empty brake cylinder, as above described. When the pressure in the empty brake cylinder and in diaphragm chamber 53 is thus reduced a degree slightly exceeding the proportionate degree of increase in auxiliary reservoir pressure acting in diaphragm chamber 54, the constant pressure of the control springs 93 and 94 overcomes the opposing, reduced brake cylinder pressure in chamber 56 acting on the differential areas of diaphragms 53 and and the auxiliary reservoir. pressure in chamber 53 acting on diaphragm 53, and defleets said diaphragms so as to move the release valve seat 84 into engagement with the release valve 32 and thereby prevent further venting of fluid under pressure from the empty brake cylinder.

When it desired to effect another step ofreduction in brake cylinder pressure, the brake pipe pressure is again increased an amount according to thedegree of release desired. The conse quent increase in auxiliary reservoir pressure in diaphragm chamber 54 then causes the brake cylinder pressure control mechanism to again operate to effect a further and proportionate reduction in pressure in the empty brake cylinder I. In this manner the pr ssure in the empty brake cylinder may he graduated oil or reduced in steps according to the steps of increase in brake pipe pressure, as desire-d.

Since chamber 39 at oneside of the inshot valve piston communicates through passages cl-I and 5! with the brake cylinder chamber 55 in the control valve mechanism 3, the pressure in chamber 39 reduces as the brake cylinder pressure reduces and when reduced to a predetermined degree, spring 36 returns said piston to its normal position as shown in the drawing. This movement of piston 30 to its normal position unseats the check valve 26, preparatory to a subsequent application of the brakes.

When the triple valve device is moved to release position, communication is established between diaphragm chamber I21 and the empty brake cylinder, as hereinbefore described, so that fluid at brake, cylinder pressure will act in said chamber on diaphragm I23 to maintain the detent I08 in locking engagement with rack I05 and also to maintain the bias spring MI compressed and inefiective. The pressure in the diaphragm chamber I21 reduces however with brake cylinder pressure, as the brakes arereleased, and when reduced to a predetermined low degree, just balances the opposing pressure of the bias spring I 4 I Then upon further reduction in brake cylinder pressure acting on diaphragm I23, the bias spring I II predominates and is adapted to rotate the lever MI in a counter-clockwise direction so as to move the hook-like portion I 31 of the arms 436 of lever I 34 into engagement with pins 38 on sleeve and apply pressure to said pins which aids the auxiliary reservoir pressure in chamber 54 acting on diaphragm 53 to move the sleeve 90 and follower member 52 to the release position. The pressure thus applied to sleeve 90 by the bias spring I4I increases as the opposing brake cylinder pressure in diaphragm chamber I21 acting on diaphragm I23 reduces, so that at the time the fluid under pressure is completely vented from the brake cylinder and the auxiliary reservoir pressure acting on diaphragm 53 is increased to normal and balances the pressure of the control springs 93 and 94, the brake cylinder pressure control mechanism is held in its release position by the full pressure of the bias spring HI applied through the lever I31, link I26 and lever I34;

When the pressure of the bias spring I 4| on one end of the operating bar I I4 becomes reduced, in the manner above described, to below the 0pposing pressure of the detent spring II8 acting on the other end, the spring II8 acting through the bell crank lever H2 moves the diaphragm follower I22 and diaphragm I23 back to the normal position and in so doing pulls the detent I08 out of locking engagement with the rack I05. With the rack I thus free to move, the auxiliary reservoir pressure acting in chamberv 95 controls the pressure of the control springs 93 and 94 until a subsequent application. of the;

brakes is efiected.

In controlling a train, provided with this .improved equipment, down a. descending grade, the brakes will be alternately applied, then partially released, and then reapplied, butin releasing, the brake cylinder pressure will never be reduced to as low a pressure as required to permit unlocking of the detent I08 from the rack I05, so that the pressure of the control springs 93 and 94 will remain the same during the entire descent of the grade. As a result, the same brake cylinder pressure will be obtained upon the last reduction effected in brake pipepressure near the foot of the grade as was obtained upon the initial reduction in brake pipe pressure upon starting the descent of the grade.

It will-be noted that the control springs 93 and 3-1 are adjusted, when the brakes are released, to exert a pressure on the diaphragm 59 equal to the pressure of fluid obtained in the auxiliary reservoir, which corresponds to the pressure of fluid in the brake pipe, so that the pressure of said control springs will automatically vary 'according to the brake pipe pressure carried. It is well known that, due to brake pipe leakage, the pressure of fluid obtained in the difierent parts of a train varies, that is, if it is intended to carry seventy pounds pressure in the brake pipe, this pressure will be obtained at the front end of the train but if there is brake pipe leakage, the pressure obtained in the brake pipe at the rear end'of the train will be somewhat less. However; irrespective of the degree of brake pipe pressure, the control springs 93 and 94 will be adjusted to exert a corresponding pressure on the diaphragm 59, and since the springs 93 and 94 are locked in their adjusted position immediately upon initiating an application of the brakes, the pressure of said springs on diaphragm 59 will remain'constant during the entire period that the brakes are applied.

It will now be noted'that an improved fluid pressure brake equipment is provided having control springs adjusted according to the brake pipe pressure, while the brakes are released, to control the pressure obtained in the brake cylinder according to the reduction or increase in brake pipe pressure. These control springs are locked in their adjusted position immediately upon initiating a reduction in brake pipe pressure and are maintained locked in their adjusted position until, upon effecting a release of the brakes, the brake cylinder pressure is substantially fully released, so that, while the brakes are applied, the pressure acting in the brake cylinder will bear a predetermined relation to the degree of reduction in brake pipe pressure irrespective of the length of time which the brakes are maintained applied, and irrespective of variations in the travel of the brake cylinder piston or leakage of fluid under pressure from the brake cylinder within a permissible degree. A further feature of the invention lies in the spring biasing means which become operative upon the brake cylinder pressure control mechanism, when the brake cylinder pressure is reduced'to a predetermined low degree, to ensure movement of'said mechanism to release position for effecting a complete release of fluid under pressure from the brake cylinder. The pressure of the spring biasing means is removed from the brake cylinder pressure control mechanism when the brake cylinder pressure exceeds the predetermined low degree, above mentioned, in order not to influence the operation of said mechanism to maintain the proper relation between brake cylinder pressure and brake pipe reduction, when the brakes are applied.

The inshot valve device I! for controlling the build up of brake cylinder pressure in efiecting an application or the brakes is claimed in my pending application Serial No. 612,465, filed May 20, 1932, and the subject matter relating to the brake cylinder pressure control valve mechanism 3 is broadly claimed in my pending application Serial No. 631,191, filed August 31, 1932.

While one illustrative embodiment of the inventicn has been described in detail, it is not my intention to limit its scopeto that embodiment or otherwise than by the terms of the appended claims.

Having now described my invention, what I claim as new and desire tosecure by Letters Patent, is: g

1. In a fluidpressure brake, the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at the pressure carried in said brake pipe, and a brake cylinder to which fluid under pressure is supplied from said auxiliary reservoir for applying the brakes upon a reduction in brake pipe pressure and from which fluid under pressure is vented to releasethe brakes upon an increase in brake pipe pressure, of valve means for regulating the pressure obtained in said brake cylinder in accordance with the degree of reduction and increase in brake pipe pressure, pressure exerting means for controlling the operation of said valve means, means for adjusting the pressure of said pressure exerting means according to the pressure obtained in the auxiliary reservoir when the brakes are released, and means operated by auxiliary reservoir pressure upon a reduction in brake pipe pressure for looking said pressureexerting means in the adjusted condition upon eiiecting a reduction in brake pipe pressure, and operated by brake cylinder pressure upon an increase in brake pipe pressure for maintaining said pressure exerting means locked in the adjusted condition.

2. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at the pressure carried in said brake pipe, and a brake cylinder to which fluid under pressure is supplied from said auxiliary reservoir for applying the brakes upon a reduction in brake pipe pressure, and from which fluid under pressure is vented to eflect a release of the brakes upon an increase in brake pipe pressure, of valve means for regulating the pressure in said brake cylinder in accordance with the degree of reduction and increase in brake pipe pressure, continually acting pressure exerting means for controlling the operation of said valve means, means operated by auxiliary reservoir pressure when the brakes are released for adjusting the acting pressure of said pressure exerting means and means operative by auxiliary reservoir pressure upon a reduction in brake pipe pressure and by brake cylinder pressure upon an increase in brake pipe pressure for locking said pressure exerting means in the adjusted condition.

3. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at the pressure carried in said brake pipe, and a brake cylinder to which fluid under pressure is supplied from said auxiliary reservoir for applying the brakes upon a reduction in brake pipe pressure, and from which fluid under pressure is vented to effect a release of the brakes upon an increase in brake pipe pressure, of valve means for regulating the pressure in said brake cylinder in accordance with the degree of reduction and increase in brake pipe pressure, continually acting pressure exerting means for controlling the operation of said valve means, means operated by auxiliary reservoir pressure when the brakes are released for adjusting the acting pressure of said pressure exerting means and means operative by auxiliary reservoir pressure upon initiating a reduction in brake pipe pressure and by brake cylinder pressure until the brake cylinder pressure is substantially completely vented upon an increase in brake pipe pressure for locking said pressure exerting means in the adjusted condition.

4. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at the pressure carried in said brake pipe, and a brake cylinder to which fluid under pressure is supplied from said auxiliary reservoir for applying the brakes upon a reduction in brake pipe pressure, and from which fluid under pressure is vented to effect a release of the brakes upon an increase in brake pipe pressure, of valve means subject to the pressures of fluid in said brake cylinder and auxiliary reservoir for regulating the pressure in said brake cylinder in accordance with the degree of reduction and increase in brake pipe pressure, continually acting pressure exerting means opposing the pressures of fluid in said brake cylinder and auxiliary reservoir on said valve means, means for adjusting the pressure of said pressure exerting means in accordancewith the pressure in said auxiliaryreservoir when the brakes arereleased, and means operatedby auxiliary reservoir pressure in effecting anapplication of thebrakes and by brake cylinder pressure in efiecting a release of the brakes for locking said pressure exerting means in the adjusted condition Y 5. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir, normally charged with fluid underpressurefrom saidbrake pipe, and abrake cylinder to which fluid under pressure is supplied from the auxiliary reservoir upon a reduction in, brake pipe pressure to apply the brakes, and from which fluid under pressure is vented upon an increasein brake pipepressure to release the brakes, and valvcmeans subject to brake cylinder pressure and, fluid under brake pipe pressure operative-toregulate the pressure in said brake cylinder according to the degree of reduction and increase in brakepipe pressure,

the brakes and until thebrakes are substantially released.

6. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir normal- 1y charged with fluid under'pressure from said brake pipe, and a. brake cylinder to which fluid under pressure is supplied from the auxiliary reservoir upon a reduction in brake pipe pressure to apply the brakes, and from which fluid under pressure is vented upon an increase in brake pipe pressure to release the brakes, and valve means subject to brake cylinder pressure and: fluid under brake pipe pressur operative to regulate the pressure in said brake cylinder according to the degree of reduction and increase inbrake pipe pressure, spring means acting on said valve means in opposition to said brake cylinder pressure and said fluid under brake pipe pressure, a movable abutment subject to auxiliary reservoir pressure for varying the pressure of said spring means on said valve means according to the pressure obtained in the auxiliary reservoir when the brakes are released, a member associated with said abutment and movable thereby to a position to correspond to the adjustment of said spring means, locking means movable by fluid under pressure into locking engagement with said member upon a reduction in brake pipe pressure, a valve device controlled by brake pipe pressure and operative upon a reduction in brake pipe pressure to supply fluid under pressure for effecting the operation of said locking means and operative upon an increase in brake pipe pressure to supply fluid under pressure from said brake cylinder for effecting the operation 01 said locking means and means operative when the brake cylinder pressure is reduced to a predetermined degree to move said locking means out of locking engagement with said member.

7. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir, a brake cylinder and a valve device subject to the opposing pressures of the brake pipe and auxiliary reservoir and operative upon a reduction in brake pipe pressure to supply fluid under pressure from said auxiliary reservoir to said brake cylinder to apply the brakes, andoperative upon-an increase in brake pipe pressure to supply fluidunder pressure fromsaid brake pipe to said auxiliary reservoir, oivalve means-subjecttobrake 'cylinderpressure and fluidunder brake P pe pressure for regulating the pressure in said brake cylinder in accordance with the reduction and increase in brake pipe pressure and operative upon an increase in brake .pipe pressure to vent fluid under pressure from said brake cylinder to effect a releaseofthe brakes, a spring atall times under compression opposing the pressures of said brake cylinder and fluid; under brake. pipe pressure on said valve means for controlling the operation of said valve means, a movable abutment associated with said spring, said movable abutment being subject to auxiliary reservoir pressure and movable thereby to exert acorrespondingpressureon said spring,

a member associated withsaid abutment and positioned according to the pressure of said spring, means movable by fluid under pressure into locking enga ement with said member, and a movable abutment for moving said means, said valve device being operative upon a reduction in brake pipe pressure to supply fluid under brake pipe pressure for operating thelast mentioned abutment to move said means into locking engagement with said member and operative upon an increase in brake pipe pressure to supply fluid under pressure from said brake cylinder for operating the last mentioned abutment to holdsaidmeans in looking: engagement, with said, member, and a spring operative when the brake-cylinder pressure is reduced to a predetermined low degree f or moving said means out of locking engagement with said member..

i 4 s. In a nuid ressurebrake, the combination with a brake pipe, an auxiliary reservoir normally charged with'fluid under pressure from said brakepipe, and a brake cylinder, to which fluid under pressure is supplied fromv the auxiliary reservoir upon a reduction in brake pipe pressure to apply, the brakes, and iromswhich fluid under pressure is vented uponan increase in brake pipe pressured-o release the brakes, and valve means subject-to brake cylinder pressure and fluid under brake pipe pressure? operative to regulate .the pressure in saidbrake cylinder. according to the pressure of fluid in the auxiliary reservoir, a rack associated with the last mentioned abutment and movable thereby to a position corresponding to the degree of compression of said spring, a detent movable into and out of locking engagement with said rack, an abutment operated by fluid under brake pipe pressure in effecting an application of the brakes for moving said detent into locking engagement with said rack and operated by fluid under pressure from the brake cylinder in effecting a release of the brakes for holding said detent in locking engagement with said rack, valve means operated in accordance with the reduction and increase in brake pipe pressure for establishing the communication through which fluid under pressure is supplied for operating said abutment, and a spring for moving said detent out of locking engagement with said rack upon a substantially complete venting of fluid under pressure from the brake cylinder. r g

9. In a fluid pressure-brake, the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at brake pipe pressure and a brake cylinder to which fluid under-pressure is supplied from said auxiliary reservoir to apply the brakes upon a reduction in brake pipe pressure, valve means subject-to brake cylinder pressure and auxiliary reservoir pressure and movable by an increase in auxiliary reservoir pressure to a release position for venting fluid under pressure from said brake cylinder, and movable upon a reduction in brake cylinder pressure in proportion tothe increase in auxiliary reservoir pressure to anotherposition for closing the communication through which fluid under pressure is vented from the brake cylinder, constant pressure means opposing the brake cylinder and auxiliary reservoir pressures on said valve means with a pressure equal to auxiliary reservoir pressure when the brakes are released for controlling the operation of said valve means, a spring acting on said valve means for moving said valve means to said release 7 position, and means operated by fluid atbrake pipe pressure when the brakes are applied for rendering said spring ineffective.

10. In a fluid pressure brake,'the combination with a brake pipe, an auxiliary reservoir normally charged with fluid at brake pipe pressure and a brake cylinder to which fluid under pressure is supplied from said auxiliary reservoirto' apply the brakes upon a reduction in brake pipe pressure, valve means subject to brake cylinder pressure and auxiliary reservoir pressure and movable by an increasein auxiliary reservoir pressure to a release position for venting fluid under pressure from said brake cylinder, and movable upon a reduction in brake cylinder pressure in proportion to the increase in auxiliary reservoir pressure to another position for closing the communication through which fluid under pressure is vented from thebrake cylinder, constant pressure -means opposing the brake cylinder and auxiliary reservoir pressures on said valve means with a pressure equal to auxiliary reservoir pressure when the brakes are released for controlling the operation of said valvemeans, a spring acting on said valve means .for moving said valve means to said release position, means operatedby fluid at brake pipe pressure upon effecting an application of the brakes and by brake cylinder pressure upon effecting a release of the brakes for rendering said spring ineflective, and a valve device operative in accordance with variations in brake pipe-pressure for establishing the communication through which fluid under pressure is supplied for efiecting the operation of said means.

11. In a fluid pressure brake, the combination with a brake pipe, an auxiliary reservoir and a brake cylinder, of a valve device operated upon a reduction in brake pipe pressure to supply fluid under pressure from said auxiliary reservoir to said brake cylinder to apply the brakes and operative upon an increase in brake pipe pressure to supply fluid under pressure from said brake pipe to said auxiliary reservoir, valve means subject to auxiliary reservoir pressure and brake cylinder pressure'for regulating the pressure in said brake cylinder in accordance with the reduction in brake pipe pressure and for venting fluid under pressure from said brake cylinder upon an increase in brake pipe pressure, continually acting pressure exerting means opposing the pressure of the brake r cylinder and auxiliary reservoir on said valve means for controlling the operation thereof, means for adjusting the pressure of said pressure exerting means according to the pressure in said auxiliary reservoir when the brakes are released, a member for locking said means in the adjusted condition, spring means for moving said valve means to the position for venting the brake cylinder,a movable abutment operated by fluid under pressure for efiecting the operation of said member to lock said means in the adjusted condition and for rendering said spring means ineirective said valve device being operative upon a reduction in brake pipe pressure to supply fluid under brake pipe pressure for efiecting the operation of said movable abutment and upon an increase in'brake pipe pressure to supply fluid under pressure from said brake cylinder for effecting the operation of said movable abutment, and spring means operated when the brake cylinder pressure acting on said movable abutment is reduced to a predetermined degree for operating said member to unlock said means.

CLYDE C. FARMER. 

